Multi-speed transmission

ABSTRACT

A transmission is provided having an input member, an output member, four planetary gear sets, a plurality of coupling members and a plurality of torque transmitting devices. Each of the planetary gear sets includes first, second and third members. The torque transmitting devices may include clutches and brakes.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application claims the benefit of U.S. Provisional Application No.60/900,613 filed on Feb. 8, 2007. The disclosure of the aboveapplication is incorporated herein by reference.

TECHNICAL FIELD

The invention relates generally to a multiple speed transmission havinga plurality of planetary gear sets and a plurality of torquetransmitting devices and more particularly to a transmission having nineor more speeds, four planetary gear sets and a plurality of torquetransmitting devices.

BACKGROUND

The statements in this section merely provide background informationrelated to the present disclosure and may or may not constitute priorart.

A typical multiple speed transmission uses a combination of frictionclutches, planetary gear arrangements and fixed interconnections toachieve a plurality of gear ratios. The number and physical arrangementof the planetary gear sets, generally, are dictated by packaging, costand desired speed ratios.

While current transmissions achieve their intended purpose, the need fornew and improved transmission configurations which exhibit improvedperformance, especially from the standpoints of efficiency,responsiveness and smoothness and improved packaging, primarily reducedsize and weight, is essentially constant. Accordingly, there is a needfor an improved, cost-effective, compact multiple speed transmission.

SUMMARY

A transmission is provided having an input member, an output member,four planetary gear sets, a plurality of coupling members and aplurality of torque transmitting devices. Each of the planetary gearsets includes first, second and third members. The torque transmittingdevices may include clutches and brakes.

One embodiment of the present invention includes an input member, anoutput member, first, second, third and fourth planetary gear sets eachhaving first, second and third members, a first interconnecting membercontinuously interconnecting the third member of the first planetarygear set with the first member of the second planetary gear set, asecond interconnecting member continuously interconnecting the thirdmember of the second planetary gear set with the second member of thethird planetary gear set, a third interconnecting member continuouslyinterconnecting the third member of the third planetary gear set withthe second member of the fourth planetary gear set, and a fourthinterconnecting member continuously interconnecting the first member ofthe third planetary gear set with the first member of the fourthplanetary gear set. Six torque transmitting mechanisms are selectivelyengageable to interconnect one of the first, second, and third memberswith another of the first, second, third members, and a stationaryelement. The torque transmitting mechanisms are selectively engageablein combinations of at least three to establish at least nine forwardspeed ratios and at least one reverse speed ratio between the inputmember and the output member.

In one aspect of the present invention, a first of the six torquetransmitting mechanisms is selectively engageable to interconnect thesecond member of the first planetary gear set with the second member ofthe second planetary gear set.

In another aspect of the present invention, a second of the six torquetransmitting mechanisms is selectively engageable to interconnect thesecond member of the second planetary gear set with the third member ofthe fourth planetary gear set.

In yet another aspect of the present invention, a third of the sixtorque transmitting mechanisms is selectively engageable to interconnectat least one of the input member and the second member of the firstplanetary gear set with at least one of the first member of the thirdplanetary gear set and the first member of the fourth planetary gearset.

In yet another aspect of the present invention, a fourth of the sixtorque transmitting mechanisms is selectively engageable to interconnectat least one of the third member of the first planetary gear set and thefirst member of the second planetary gear set with at least one of thefirst member of the third planetary gear set and the first member of thefourth planetary gear set.

In yet another aspect of the present invention, a fifth of the sixtorque transmitting mechanisms is selectively engageable to interconnectthe first member of the first planetary gear set with the stationaryelement.

In yet another aspect of the present invention, a sixth of the sixtorque transmitting mechanisms is selectively engageable to interconnectthe third member of the fourth planetary gear set with the stationaryelement.

In yet another aspect of the present invention, the first members aresun gears, the second members are carrier members, and the third membersare ring gears.

In yet another aspect of the present invention, the input member iscontinuously interconnected with the second member of the firstplanetary gear set and wherein the output member is continuouslyinterconnected with the second member of the fourth planetary gear set.

In yet another aspect of the present invention, two of the torquetransmitting mechanisms are brakes and four of the torque transmittingmechanisms are clutches.

In yet another aspect of the present invention, the stationary elementis a transmission housing.

Another embodiment of the transmission includes an input member, anoutput member, first, second, third and fourth planetary gear sets eachhaving a sun gear, a carrier member, and a ring gear, wherein the inputmember is continuously interconnected with the carrier member of thefirst planetary gear set and wherein the output member is continuouslyinterconnected with the carrier member of the fourth planetary gear set,a first interconnecting member continuously interconnecting the ringgear of the first planetary gear set with the sun gear of the secondplanetary gear set, a second interconnecting member continuouslyinterconnecting the ring gear of the second planetary gear set with thecarrier member of the third planetary gear set, a third interconnectingmember continuously interconnecting the ring gear of the third planetarygear set with the carrier member of the fourth planetary gear set, and afourth interconnecting member continuously interconnecting the sun gearof the third planetary gear set with the sun gear of the fourthplanetary gear set. A first torque transmitting mechanism is selectivelyengageable to interconnect the carrier member of the first planetarygear set with the carrier member of the second planetary gear set, asecond torque transmitting mechanism is selectively engageable tointerconnect the carrier member of the second planetary gear set withthe ring gear of the fourth planetary gear set, a third torquetransmitting mechanism is selectively engageable to interconnect atleast one of the input member and the carrier member of the firstplanetary gear set with at least one of the sun gear of the thirdplanetary gear set and the sun gear of the fourth planetary gear set, afourth torque transmitting mechanism is selectively engageable tointerconnect at least one of the ring gear of the first planetary gearset and the sun gear of the second planetary gear set with at least oneof the sun gear of the third planetary gear set and the sun gear of thefourth planetary gear set, a fifth torque transmitting mechanism isselectively engageable to interconnect the sun gear of the firstplanetary gear set with a stationary element, and a sixth torquetransmitting mechanism is selectively engageable to interconnect thering gear of the fourth planetary gear set with the stationary element.The torque transmitting mechanisms are selectively engageable incombinations of at least three to establish at least nine forward speedratios and at least one reverse speed ratio between the input member andthe output member.

The above features and advantages and other features and advantages ofthe present invention are readily apparent from the following detaileddescription of the best modes for carrying out the invention when takenin connection with the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

The drawings described herein are for illustration purposes only and arenot intended to limit the scope of the present disclosure in any way.

FIG. 1 is a lever diagram of an embodiment of a multiple speedtransmission according to the present invention;

FIG. 2 is a diagrammatic view of an embodiment of a multiple speedtransmission according to the present invention;

FIG. 3 is a truth table presenting the state of engagement of thevarious torque transmitting elements in each of the available forwardand reverse speeds or gear ratios of the transmission illustrated inFIGS. 1 and 2; and

FIG. 4 is an alternate truth table presenting the state of engagement ofthe various torque transmitting elements in each of the availableforward and reverse speeds or gear ratios of the transmissionillustrated in FIGS. 1 and 2.

DESCRIPTION

At the outset, it should be appreciated that the automatic transmissionof the present invention has an arrangement of permanent mechanicalconnections between the elements of the four planetary gear sets incommon. These mechanical connections generically link or relatetransmission embodiments. A first component or element of a firstplanetary gear set is permanently coupled to a first component orelement of a second planetary gear set. A third component or element ofthe second planetary gear set is permanently coupled to a secondcomponent or element of a third planetary gear set. A first component orelement of the third planetary gear set is permanently coupled to afirst component or element of a fourth planetary gear set. Finally, athird component or element of the third planetary gear set ispermanently coupled to a second component or element of the fourthplanetary gear set.

Referring now to FIG. 1, an embodiment of a multiple speed transmission10 is illustrated in a lever diagram format. A lever diagram is aschematic representation of the components of a mechanical device suchas an automatic transmission. Each individual lever represents aplanetary gear set wherein the three basic mechanical components of theplanetary gear are each represented by a node. Therefore, a single levercontains three nodes: one for the sun gear, one for the planet gearcarrier, and one for the ring gear. The relative length between thenodes of each lever can be used to represent the ring-to-sun ratio ofeach respective gear set. These lever ratios, in turn, are used to varythe gear ratios of the transmission in order to achieve an appropriateratios and ratio progression. Mechanical couplings or interconnectionsbetween the nodes of the various planetary gear sets are illustrated bythin, horizontal lines and torque transmitting devices such as clutchesand brakes are presented as interleaved fingers. If the device is abrake, one set of the fingers is grounded. Further explanation of theformat, purpose and use of lever diagrams can be found in SAE Paper810102, “The Lever Analogy: A New Tool in Transmission Analysis” byBenford and Leising which is hereby fully incorporated by reference.

The transmission 10 includes an input shaft or member 12, an outputshaft or member 14, a first planetary gear set 16 having three nodes: afirst node 24, a second node 26 and a third node 28, a second planetarygear set 18 having three nodes: a first node 42, a second node 44 and athird node 46, a third planetary gear set 20 having three nodes: a firstnode 52, a second node 54 and a third node 56, and a fourth planetarygear set 22 having three nodes: a first node 72, a second node 74 and athird node 76.

The input member 12 is coupled to the third node 28 of the firstplanetary gear set 16. The output 14 is coupled to the third node 76 ofthe fourth planetary gear set 22. The second node 26 of the firstplanetary gear set 16 is coupled to the first node 42 of the secondplanetary gear set 18. The second node 44 of the second planetary gearset 18 is coupled to the third node 56 of the third planetary gear set20. The first node 52 of the third planetary gear set 20 is coupled tothe first node 72 of the fourth planetary gear set 22. The second node54 of the third planetary gear set 20 is coupled to the third node 76 ofthe fourth planetary gear set 22.

A first clutch 80 selectively connects the third node 28 of the firstplanetary gear set 16 to the third node 46 of the second planetary gearset 18. A second clutch 82 selectively connects the third node 46 of thesecond planetary gear set 18 to the second node 74 of the fourthplanetary gear set 22. A third clutch 84 selectively connects the inputmember 12 to the first node 52 of the third planetary gear set 20. Afourth clutch 86 selectively connects the first node 42 of the secondplanetary gear set 18 to the first node 52 of the third planetary gearset 20. A first brake 90 selectively connects the first node 24 of thefirst planetary gear set 16 to a ground, stationary element, or atransmission housing 100. A second brake 92 selectively connects thesecond node 74 of the fourth planetary gear set 22 to a ground,stationary element, or the transmission housing 100.

Referring now to FIG. 2, a stick diagram presents a schematic layout ofthe embodiment of the multiple speed transmission 10 according to thepresent invention. In FIG. 2, the numbering from the lever diagram ofFIG. 1 is carried over. The clutches, brakes and couplings arecorrespondingly presented whereas the nodes of the planetary gear setsnow appear as components of planetary gear sets such as sun gears, ringgears, planet gears and planet gear carriers.

For example, the first planetary gear set 16 includes a sun gear member24, a ring gear member 26 and a carrier member 28 that rotatablysupports a set of pinion gears 30 (only one shown). Each of the piniongears 30 are configured to intermesh with both sun gear member 24 andring gear member 26. Sun gear member 24 is connected for common rotationwith a first interconnecting shaft or member 32. Ring gear member 26 isconnected for common rotation with a second interconnecting shaft ormember 34. Carrier member 28 is connected for common rotation with athird interconnecting shaft or member 36 and with input shaft 12.

The second planetary gear set 18 includes a sun gear member 42, a ringgear member 44 and a carrier member 46 that rotatably supports a set ofpinion gears 48. Each of the pinion gears 48 are configured to intermeshwith both sun gear member 42 and ring gear member 44. Sun gear member 42is connected for common rotation with a fourth interconnecting shaft ormember 38. Ring gear member 44 is connected for common rotation with afifth interconnecting shaft or member 50. Carrier member 46 is connectedfor common rotation with a sixth interconnecting shaft or member 60.

The third planetary gear set 20 includes a sun gear member 52, a ringgear member 54 and a carrier member 56 that rotatably supports a set ofpinion gears 58. Each of the pinion gears 58 are configured to intermeshwith both sun gear member 52 and ring gear member 54. Sun gear member 52is connected for common rotation with a seventh interconnecting shaft ormember 62. Ring gear member 54 is connected for common rotation with aneighth interconnecting shaft or member 64. Carrier member 56 isconnected for common rotation with fifth interconnecting member 50.

The fourth planetary gear set 22 includes a sun gear member 72, a ringgear member 74 and a carrier member 76 that rotatably supports a set ofpinion gears 78. Each of the pinion gears 78 are configured to intermeshwith both sun gear member 72 and ring gear member 74. Sun gear member 72is connected for common rotation with seventh interconnecting member 62.Ring gear member 74 is connected for common rotation with a ninthinterconnecting shaft or member 66. Carrier member 76 is connected forcommon rotation with eighth interconnecting member 64 and with outputshaft 14.

The input shaft 12 is continuously connected to an engine (not shown) orto a turbine of a torque converter (not shown). The output shaft 14 iscontinuously connected with the final drive unit (not shown).

The transmission 10 includes a variety of torque-transmitting mechanismsor devices including a first clutch 80, a second clutch 82, a thirdclutch 84, a fourth clutch 86, a first brake 90 and a second brake 92.First clutch 80 is selectively engagable to connect thirdinterconnecting member 36 to sixth interconnecting member 60. Secondclutch 82 is selectively engagable to connect sixth interconnectingmember 60 to ninth interconnecting member 66. Third clutch 84 isselectively engagable to connect input shaft 12 to seventhinterconnecting member 62. Fourth clutch 86 is selectively engagable toconnect second and fourth interconnecting members 34, 38 to seventhinterconnecting member 62. First brake 90 is selectively engagable toconnect first interconnecting member 32 to transmission housing 100 torestrict rotation of first interconnecting member 32 and sun gear 24relative to housing 100. Second brake 92 is selectively engagable toconnect ninth interconnecting member 66 to housing 100 to restrictrotation of ninth interconnecting member 66 and ring gear 74 relative tohousing 100.

Referring now to FIGS. 2 and 3, the operation of the embodiment of themultiple speed transmission 10 will be described. It will be appreciatedthat the transmission 10 is capable of transmitting torque from theinput shaft or member 12 to the output shaft or member 14 in at leastnine forward speed or torque ratios and at least one reverse speed ortorque ratio. Each forward and reverse speed or torque ratio is attainedby engagement of one or more of the torque-transmitting mechanisms (i.e.first clutch 80, second clutch 82, third clutch 84, fourth clutch 86,first brake 32, and second brake 34), as will be explained below. FIG. 3is a truth table presenting the various combinations oftorque-transmitting mechanisms or elements that are activated or engagedto achieve the various gear states. Actual numerical gear ratios andgear steps of the various gear states are also presented although itshould be appreciated that these numerical values are exemplary only andthat they may be adjusted over significant ranges to accommodate variousapplications and operational criteria of the transmission 10. An exampleof the gear ratios that may be obtained using the embodiments of thepresent invention are also shown in FIG. 3. Of course, other gear ratiosare achievable depending on the gear diameter, gear teeth count and gearconfiguration selected.

To establish reverse gear, the first brake 90, the second brake 92, andthe second clutch 82 are engaged or activated. First brake 90 connectsfirst interconnecting member 32 to transmission housing 100 to restrictrotation of first interconnecting member 32 and sun gear 24 relative tohousing 100. Second brake 92 connects ninth interconnecting member 66 tohousing 100 to restrict rotation of ninth interconnecting member 66 andring gear 74 relative to housing 100. Second clutch 82 connects sixthinterconnecting member 60 to ninth interconnecting member 66. Likewise,the nine forward ratios are achieved through different combinations ofclutch and brake engagement, as shown in FIG. 3.

Referring now to FIG. 4, an alternate truth table is presented for theoperation of the embodiment of the multiple speed transmission 10. Itwill be appreciated that the transmission 10 is capable of transmittingtorque from the input shaft or member 12 to the output shaft or member14 in at least ten forward speed or torque ratios and at least onereverse speed or torque ratio. Each forward and reverse speed or torqueratio is attained by engagement of one or more of thetorque-transmitting mechanisms (i.e. first clutch 80, second clutch 82,third clutch 84, fourth clutch 86, first brake 32, and second brake 34),as was described above. Actual numerical gear ratios and gear steps ofthe various gear states are also presented although it should beappreciated that these numerical values are exemplary only and that theymay be adjusted over significant ranges to accommodate variousapplications and operational criteria of the transmission 10. An exampleof the gear ratios that may be obtained using the embodiments of thepresent invention are also shown in FIG. 3. Of course, other gear ratiosare achievable depending on the gear diameter, gear teeth count and gearconfiguration selected.

It will be appreciated that the foregoing explanation of operation andgear states of the multiple speed transmission 10 assumes, first of all,that all the clutches and the brakes not specifically referenced in agiven gear state are inactive or disengaged and, second of all, thatduring gear shifts, i.e., changes of gear state, between at leastadjacent gear states, a clutch or brake engaged or activated in bothgear states will remain engaged or activated. Additionally, the presentinvention contemplates that downshifts follow essentially the reversesequence of the corresponding upshift (as described above), and severalpower-on skip-shifts are possible (e.g. from 1st to 3rd).

While the best modes for carrying out the invention have been describedin detail, those familiar with the art to which this invention relateswill recognize various alternative designs and embodiments forpracticing the invention within the scope of the appended claims.

1. A transmission comprising: an input member; an output member; first,second, third and fourth planetary gear sets each having first, secondand third members; a first interconnecting member continuouslyinterconnecting the third member of the first planetary gear set withthe first member of the second planetary gear set; a secondinterconnecting member continuously interconnecting the third member ofthe second planetary gear set with the second member of the thirdplanetary gear set; a third interconnecting member continuouslyinterconnecting the third member of the third planetary gear set withthe second member of the fourth planetary gear set; a fourthinterconnecting member continuously interconnecting the first member ofthe third planetary gear set with the first member of the fourthplanetary gear set; and six torque transmitting mechanisms selectivelyengageable to interconnect one of the first, second, and third memberswith another of the first, second, third members, and a stationaryelement, and wherein the torque transmitting mechanisms are selectivelyengageable in combinations of at least three to establish at least nineforward speed ratios and at least one reverse speed ratio between theinput member and the output member.
 2. The transmission of claim 1wherein a first of the six torque transmitting mechanisms is selectivelyengageable to interconnect the second member of the first planetary gearset with the second member of the second planetary gear set.
 3. Thetransmission of claim 2 wherein a second of the six torque transmittingmechanisms is selectively engageable to interconnect the second memberof the second planetary gear set with the third member of the fourthplanetary gear set.
 4. The transmission of claim 3 wherein a third ofthe six torque transmitting mechanisms is selectively engageable tointerconnect at least one of the input member and the second member ofthe first planetary gear set with at least one of the first member ofthe third planetary gear set and the first member of the fourthplanetary gear set.
 5. The transmission of claim 4 wherein a fourth ofthe six torque transmitting mechanisms is selectively engageable tointerconnect at least one of the third member of the first planetarygear set and the first member of the second planetary gear set with atleast one of the first member of the third planetary gear set and thefirst member of the fourth planetary gear set.
 6. The transmission ofclaim 5 wherein a fifth of the six torque transmitting mechanisms isselectively engageable to interconnect the first member of the firstplanetary gear set with the stationary element.
 7. The transmission ofclaim 6 wherein a sixth of the six torque transmitting mechanisms isselectively engageable to interconnect the third member of the fourthplanetary gear set with the stationary element.
 8. The transmission ofclaim 1 wherein the first members are sun gears, the second members arecarrier members, and the third members are ring gears.
 9. Thetransmission of claim 1 wherein the input member is continuouslyinterconnected with the second member of the first planetary gear setand wherein the output member is continuously interconnected with thesecond member of the fourth planetary gear set.
 10. The transmission ofclaim 1 wherein two of the torque transmitting mechanisms are brakes andfour of the torque transmitting mechanisms are clutches.
 11. Thetransmission of claim 1 wherein the stationary element is a transmissionhousing.
 12. A transmission comprising: an input member; an outputmember; first, second, third and fourth planetary gear sets each havingfirst, second and third members, wherein the input member iscontinuously interconnected with the second member of the firstplanetary gear set and wherein the output member is continuouslyinterconnected with the second member of the fourth planetary gear set;a first interconnecting member continuously interconnecting the thirdmember of the first planetary gear set with the first member of thesecond planetary gear set; a second interconnecting member continuouslyinterconnecting the third member of the second planetary gear set withthe second member of the third planetary gear set; a thirdinterconnecting member continuously interconnecting the third member ofthe third planetary gear set with the second member of the fourthplanetary gear set; a fourth interconnecting member continuouslyinterconnecting the first member of the third planetary gear set withthe first member of the fourth planetary gear set; a first torquetransmitting mechanism selectively engageable to interconnect the secondmember of the first planetary gear set with the second member of thesecond planetary gear set; a second torque transmitting mechanismselectively engageable to interconnect the second member of the secondplanetary gear set with the third member of the fourth planetary gearset; a third torque transmitting mechanism selectively engageable tointerconnect at least one of the input member and the second member ofthe first planetary gear set with at least one of the first member ofthe third planetary gear set and the first member of the fourthplanetary gear set; a fourth torque transmitting mechanism selectivelyengageable to interconnect at least one of the third member of the firstplanetary gear set and the first member of the second planetary gear setwith at least one of the first member of the third planetary gear setand the first member of the fourth planetary gear set; a fifth torquetransmitting mechanism selectively engageable to interconnect the firstmember of the first planetary gear set with a stationary element; and asixth torque transmitting mechanism selectively engageable tointerconnect the third member of the fourth planetary gear set with thestationary element, and wherein the torque transmitting mechanisms areselectively engageable in combinations of at least three to establish atleast nine forward speed ratios and at least one reverse speed ratiobetween the input member and the output member.
 13. The transmission ofclaim 12 wherein the first members are sun gears, the second members arecarrier members, and the third members are ring gears.
 14. Thetransmission of claim 13 wherein the stationary element is atransmission housing.
 15. A transmission comprising: an input member; anoutput member; first, second, third and fourth planetary gear sets eachhaving a sun gear, a carrier member, and a ring gear, wherein the inputmember is continuously interconnected with the carrier member of thefirst planetary gear set and wherein the output member is continuouslyinterconnected with the carrier member of the fourth planetary gear set;a first interconnecting member continuously interconnecting the ringgear of the first planetary gear set with the sun gear of the secondplanetary gear set; a second interconnecting member continuouslyinterconnecting the ring gear of the second planetary gear set with thecarrier member of the third planetary gear set; a third interconnectingmember continuously interconnecting the ring gear of the third planetarygear set with the carrier member of the fourth planetary gear set; afourth interconnecting member continuously interconnecting the sun gearof the third planetary gear set with the sun gear of the fourthplanetary gear set; a first torque transmitting mechanism selectivelyengageable to interconnect the carrier member of the first planetarygear set with the carrier member of the second planetary gear set; asecond torque transmitting mechanism selectively engageable tointerconnect the carrier member of the second planetary gear set withthe ring gear of the fourth planetary gear set; a third torquetransmitting mechanism selectively engageable to interconnect at leastone of the input member and the carrier member of the first planetarygear set with at least one of the sun gear of the third planetary gearset and the sun gear of the fourth planetary gear set; a fourth torquetransmitting mechanism selectively engageable to interconnect at leastone of the ring gear of the first planetary gear set and the sun gear ofthe second planetary gear set with at least one of the sun gear of thethird planetary gear set and the sun gear of the fourth planetary gearset; a fifth torque transmitting mechanism selectively engageable tointerconnect the sun gear of the first planetary gear set with astationary element; and a sixth torque transmitting mechanismselectively engageable to interconnect the ring gear of the fourthplanetary gear set with the stationary element, and wherein the torquetransmitting mechanisms are selectively engageable in combinations of atleast three to establish at least nine forward speed ratios and at leastone reverse speed ratio between the input member and the output member.16. The transmission of claim 15 wherein the stationary element is atransmission housing.